US2672223A - Self-tightening disk brake - Google Patents

Self-tightening disk brake Download PDF

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Publication number
US2672223A
US2672223A US767242A US76724247A US2672223A US 2672223 A US2672223 A US 2672223A US 767242 A US767242 A US 767242A US 76724247 A US76724247 A US 76724247A US 2672223 A US2672223 A US 2672223A
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Prior art keywords
piston
nut
rod
spring
disc
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Expired - Lifetime
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US767242A
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Butler Henry James
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Dunlop Rubber Co Ltd
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Dunlop Rubber Co Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/24—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member
    • F16D55/26—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with a plurality of axially-movable discs, lamellae, or pads, pressed from one side towards an axially-located member without self-tightening action
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D55/02—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members
    • F16D55/22—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads
    • F16D55/224—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes with axially-movable discs or pads pressed against axially-located rotating members by clamping an axially-located rotating disc between movable braking members, e.g. movable brake discs or brake pads with a common actuating member for the braking members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D65/00—Parts or details
    • F16D65/38—Slack adjusters
    • F16D65/40—Slack adjusters mechanical
    • F16D65/52—Slack adjusters mechanical self-acting in one direction for adjusting excessive play
    • F16D65/56—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut
    • F16D65/567—Slack adjusters mechanical self-acting in one direction for adjusting excessive play with screw-thread and nut for mounting on a disc brake
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0004—Parts or details of disc brakes
    • F16D2055/0062—Partly lined, i.e. braking surface extending over only a part of the disc circumference
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D55/00—Brakes with substantially-radial braking surfaces pressed together in axial direction, e.g. disc brakes
    • F16D2055/0075—Constructional features of axially engaged brakes
    • F16D2055/0091—Plural actuators arranged side by side on the same side of the rotor

Definitions

  • My invention relates to a device for automatically tightening a screwed connection of a fluid operated disc brake.
  • a device for automatically taking up slack due to wear between the faces of contacting members comprises a bolt or like element having a threaded tail portion in engagement with a complementary threaded aperture in a nut or similar element on one of said elements and being free to rotate relative to the other element and a clock-type spring .coaxially disposed with respect to said elements having one end attached to said rotatable element and the other end to a fixed point, the method of attachment of said spring being such that it tends. to cause said rotatable element to rotate in the direction which reduces the distance between the head of said boltor like element and the nut or simliarelement.
  • the invention is of particular .value for automatically taking up slack in fluid-operated disc brakes comprising piston and cylinder mechanism, an annular brake disc or discs and a friction pad or pads in light frictonal contact with the said disc or discs and adapted to be brought into firm frictional contact with said disc or discs by movementof, an operating rod associated with said piston.
  • Fig. 1 shows a plan view of oneemhi diment of the invention.
  • Fig. 2 shows a sectional view looking along. the line 2--2 of Fig. 1.
  • Figs. 3, 4, 5 show sectional views of .otherembodiments of the device.
  • Figs. 1, 2,the-radially spaced annuli 5, 6, are provided withdogs 5a, 16a .for .engagement with mating recesses eformedin the wheel disc (not shown) .the arrangementbeing such that discs 5,6 whilst beingpreventedfrom rotating independentlyof-the wheel arepermitted a slight axial movement so. .that they .can be gripped between the .pads. land :8 by movement of the backingmember 9.
  • Two diametrically opposed projecting parts 2 are formed on a circular frame member l -the projecting parts 2 being provided with enlarged extremities 2a which are hollowed out to form cylinders 21) in which pistons 3 are adapted to slide.
  • the pistons are provided with sealing rings ii] in order to form a sliding seal between each piston '3 and the wall or the cylinder 21).
  • Non rotatable piston rods i are provided,these having heads to making an interference fit within recesses 31) of the pistons.
  • A-shank portion passes axially of the projecting part 2 and extends between the inner edge of disc 5 and outer edge of disc and between pairs of inner and outer arouate pads of friction material 7, 8 which are located on either side of the discs 5, ii.
  • the friction pads T, S are composed of adjacent arcuate pads, pads i being the inner ones and pads 8 the outer ones.
  • a dust cover I l is made of spring material and suitably dished so asto act as a return spring for the piston and rod and to this end bears upon the piston end.
  • the backing member 33 has a central aperture 9a through which the non-rotatable piston rod 6 passes and a-recess within which is accommodated a nut II.
  • the end of the piston rod is screw threaded, as shown at do, to engage with similar threads formed in nut l I, the threads preferably having a quick pitch, as shown in Fig. 2.
  • the backing member 9 and nut ll together form a pressure member exerting pressure on the disc and pad when friction pad 3 is forced outwardly of its cylinder.
  • the nut i I is a circular member and is capable of rotary movement within its recess formed in the backing member 9.
  • a spiral spring .12 is disposed with one end inserted within a slot in the nut and the other to a pin [3 fixed to the backing member 9 (Fig. 2). Before securing the end to the pin it the spring is tensioned by winding it round the nut.
  • the nut has a tendency to rotate in a clock-wise direction and draw the backing member and piston together so as to reduce any to move the piston irom the position of rest.
  • each member 9 is prevented by two pins 91), shown in Fig. 1, each having one end secured to said member and extending parallel and on opposite sides of the rod 4 between the discs and 6.
  • the free end of each pin is slidably fitted in an axially extending hole in the face of the torque member 2.
  • the rod 4 is in frictional contact with the sealing members and this frictional contact prevents it from turning.
  • the nut will rotate on the threaded end of the rod 4 until stopped by engagement with the member 9 because the friction of rod 4 in contact with the supporting parts 2 and 3 is suflicient to resist the turning by reaction of the nut I I.
  • the member 9 is in frictional engagement wtih pads which prevents its turning. It will, of course, be understood that the force exerted by the spring I2 is a very light one and not sufficient to overcome these frictional resistances.
  • a slightly modified form illustrated in Fig. 3 the end of the non-rotatable rod 4 is extended beyond the nut II by a portion 4b which is provided with a slot into which the inner end of the spring I2 is inserted, the outer end being secured to a pin 13 which is secured in the nut.
  • the non-rotatable piston rod 4 makes an interference fit with a hole through the backing member 9 and is reversed so that its head 4a now bears against the backing member 9 whilst at its other end it extends through the piston 3a and terminates in a screwthreaded portion 40, which engages With the nut Ila.
  • the latter is suitably rounded on its top surface so as to fit within the curved surface of the spring cover member I4.
  • a clock type of spring I2 has its outer end secured by a pin l3 to the cover I4 whilst the inner end is secured in a slot (not shown) in the nut I lot, after threaded part 40 of the piston rod end engages with similar threads formed directly in the backing member 9 which acts as the nut.
  • the clock type spring I2 has its outer end secured by thev pin l3 to the spring cover I4 whilst the inner spring end is secured in a slot (not shown) formed in the head portion 4a.
  • the piston rod 4 is free to rotate relatively to the piston 3 so that as wear developes between the contacting parts the spring [2 by rotating the rod 4 will draw all of the operative elements together so as to reduce the clearance between them.
  • a fluid operated spot-type disc brake assembly which comprises a cylinder, a piston movable in said cylinder, said cylinder having means to stop said piston in a fixed position of rest and to admit fluid to move said piston from said position of rest to apply the brakes, an annular brake disc, a pair of axially aligned arcuate friction pads, one adjacent each face of the disc, an axially aligned operating rod actuated by said piston and cylinder mechanism having a screw threaded tail portion, a non-rotatable backing member associated with said rod and movable thereby to bring the friction pads and disc into frictional engagement, an adjusting nut rotatable on the threaded tail portion of said rod, and a clock-type spring co-axial with said rod having one end attached to a non-rotatable part of the brake assembly and the other end connected to said rod and nut assembly to rotate said nut relatively to said screw threaded tail portion to bring said friction pad into contact with said disc when said piston is in said fixed postion of rest.
  • the fluid operated spot-type disc brake assembly of claim 1 having a spring cover member closing one end of said cylinder and bearing against the piston to move said piston to said. position of rest.
  • a fluid operated spot-type disc brake assembly which comprises a cylinder, a piston movable in said cylinder, said cylinder having means to stop said piston in a fixed position of rest and to admit fluid to move said piston from said position of rest to apply the brakes, a pair of radially spaced annular brake discs, each pair having a pad on each side of an associated disc, an axially aligned operating rod actuated by said piston and cylinder mechanism having a screw threaded tail portion, a non-rotatable backing member associated with said rod and movable thereby to bring the friction pads and discs into frictional engagement, an adjusting nut rotatable on the threaded tail portion of said rod, and a clock-type spring co-axial with said rod having one end attached to a non-rotatable part of the brake assembly and the other end connected to said rod and nut assembly to rotate said nut relatively to said screw threaded tail portion to bring said friction pad into contact with said discs when said piston is in said fixed position of rest.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Braking Arrangements (AREA)

Description

March 16, 1954 H. J. BUTLER 2,672,223
SELF-TIGHTENING DISK BRAKE Filed Aug. 7, 194'? I5 Sheets-Sheet l March 16, 1954 H, BUTLER 2,672,223
SELF-TIGHTENING DISK BRAKE Filed Aug. 7, 1947 3 Sheets-Sheet 2 March 16, 1954 H, J BUTLER 2,672,223
SELF-TIGHTENING DISK BRAKE Filed Aug. 7, 1947 3 Sheets-Sheet 3 Patented Mar. 16, 1954 2,672,2 23 SELF-TIGHTENING DISK BRAKE Henry James Butler, Sutton Coldfield, England, assignor to Dunlop Rubber Company Limited, London County, England, a British company Applicatifln August 7, 1947, Serial No. 767,242
Claims priority, application Great Britain Septem 6 6 Claims. 1
My invention relates toa device for automatically tightening a screwed connection of a fluid operated disc brake.
It is an object of the invention to provide a simply constructed device adapted to ,operate in such a manner that any slack between the tapes of contacting members is taken up automatically.
According to the invention a device for automatically taking up slack due to wear between the faces of contacting members comprises a bolt or like element having a threaded tail portion in engagement with a complementary threaded aperture in a nut or similar element on one of said elements and being free to rotate relative to the other element and a clock-type spring .coaxially disposed with respect to said elements having one end attached to said rotatable element and the other end to a fixed point, the method of attachment of said spring being such that it tends. to cause said rotatable element to rotate in the direction which reduces the distance between the head of said boltor like element and the nut or simliarelement.
The invention is of particular .value for automatically taking up slack in fluid-operated disc brakes comprising piston and cylinder mechanism, an annular brake disc or discs and a friction pad or pads in light frictonal contact with the said disc or discs and adapted to be brought into firm frictional contact with said disc or discs by movementof, an operating rod associated with said piston.
In order that the invention maybe more clearly understood and carried intoeiiect .the same will be more particularly described with reference to a number ,of embodiments which are shown in the accompanying drawings. and which illustrate its application todisc brakes. comprising a piston and cylindermechanism, .twoaxially spaced annular .brake discs andiricbion pads adapted to be brought .into-fricfiiqnalcontact with the brake discs by displacement of an operating rod associated with the piston.
In the drawings:
Fig. 1 shows a plan view of oneemhi diment of the invention.
Fig. 2 shows a sectional view looking along. the line 2--2 of Fig. 1.
Figs. 3, 4, 5 show sectional views of .otherembodiments of the device.
As can be seenin Figs. 1, 2,the-radially spaced annuli 5, 6, are provided withdogs 5a, 16a .for .engagement with mating recesses eformedin the wheel disc (not shown) .the arrangementbeing such that discs 5,6 whilst beingpreventedfrom rotating independentlyof-the wheel arepermitted a slight axial movement so. .that they .can be gripped between the .pads. land :8 by movement of the backingmember 9.
Two diametrically opposed projecting parts 2 are formed on a circular frame member l -the projecting parts 2 being provided with enlarged extremities 2a which are hollowed out to form cylinders 21) in which pistons 3 are adapted to slide. The pistons are provided with sealing rings ii] in order to form a sliding seal between each piston '3 and the wall or the cylinder 21).
Non rotatable piston rods i are provided,these having heads to making an interference fit within recesses 31) of the pistons. A-shank portion passes axially of the projecting part 2 and extends between the inner edge of disc 5 and outer edge of disc and between pairs of inner and outer arouate pads of friction material 7, 8 which are located on either side of the discs 5, ii. The friction pads T, S are composed of adjacent arcuate pads, pads i being the inner ones and pads 8 the outer ones.
A dust cover I l is made of spring material and suitably dished so asto act as a return spring for the piston and rod and to this end bears upon the piston end.
One pair of inner and outer pads l, 8, of friction material is secured to the frame I and the other pair to a backing member 9. The backing member 33 has a central aperture 9a through which the non-rotatable piston rod 6 passes and a-recess within which is accommodated a nut II. The end of the piston rod is screw threaded, as shown at do, to engage with similar threads formed in nut l I, the threads preferably having a quick pitch, as shown in Fig. 2. The backing member 9 and nut ll together form a pressure member exerting pressure on the disc and pad when friction pad 3 is forced outwardly of its cylinder.
The nut i I is a circular member and is capable of rotary movement within its recess formed in the backing member 9. A spiral spring .12 is disposed with one end inserted within a slot in the nut and the other to a pin [3 fixed to the backing member 9 (Fig. 2). Before securing the end to the pin it the spring is tensioned by winding it round the nut. Looking at the deviceas represented in Fig. 1, the nut has a tendency to rotate in a clock-wise direction and draw the backing member and piston together so as to reduce any to move the piston irom the position of rest.
From the above it will be seen that when fluid pressure is applied to .the space id between the piston '3 and cylinder 12b. forthe purpose of applyin -.th .brak h stq wi co me i move away from the cylinder and exert a pull upon the rod 4 thus causing the friction pads I and 8 to press upon the discs 5, 6.
As the friction pads I and 8 wear down the nut II is tightened up by the spring I2 so as to reduce the clearance between the movable parts. The tension of the spring will be very small so that the friction pads will contact the discs very lightly and with little or no substantial friction until pressure fluid is applied to the cylinder. Rotation of each member 9 is prevented by two pins 91), shown in Fig. 1, each having one end secured to said member and extending parallel and on opposite sides of the rod 4 between the discs and 6. The free end of each pin is slidably fitted in an axially extending hole in the face of the torque member 2. The rod 4 is in frictional contact with the sealing members and this frictional contact prevents it from turning. The nut will rotate on the threaded end of the rod 4 until stopped by engagement with the member 9 because the friction of rod 4 in contact with the supporting parts 2 and 3 is suflicient to resist the turning by reaction of the nut I I. Similarly the member 9 is in frictional engagement wtih pads which prevents its turning. It will, of course, be understood that the force exerted by the spring I2 is a very light one and not sufficient to overcome these frictional resistances.
In a slightly modified form illustrated in Fig. 3 the end of the non-rotatable rod 4 is extended beyond the nut II by a portion 4b which is provided with a slot into which the inner end of the spring I2 is inserted, the outer end being secured to a pin 13 which is secured in the nut.
In the embodiment of Fig. 4 (wherein only essential features are shown) the non-rotatable piston rod 4 makes an interference fit with a hole through the backing member 9 and is reversed so that its head 4a now bears against the backing member 9 whilst at its other end it extends through the piston 3a and terminates in a screwthreaded portion 40, which engages With the nut Ila. The latter is suitably rounded on its top surface so as to fit within the curved surface of the spring cover member I4. A clock type of spring I2 has its outer end secured by a pin l3 to the cover I4 whilst the inner end is secured in a slot (not shown) in the nut I lot, after threaded part 40 of the piston rod end engages with similar threads formed directly in the backing member 9 which acts as the nut. The clock type spring I2 has its outer end secured by thev pin l3 to the spring cover I4 whilst the inner spring end is secured in a slot (not shown) formed in the head portion 4a. The piston rod 4 is free to rotate relatively to the piston 3 so that as wear developes between the contacting parts the spring [2 by rotating the rod 4 will draw all of the operative elements together so as to reduce the clearance between them.
Having decribed my invention what I claim is:
1. A fluid operated spot-type disc brake assembly which comprises a cylinder, a piston movable in said cylinder, said cylinder having means to stop said piston in a fixed position of rest and to admit fluid to move said piston from said position of rest to apply the brakes, an annular brake disc, a pair of axially aligned arcuate friction pads, one adjacent each face of the disc, an axially aligned operating rod actuated by said piston and cylinder mechanism having a screw threaded tail portion, a non-rotatable backing member associated with said rod and movable thereby to bring the friction pads and disc into frictional engagement, an adjusting nut rotatable on the threaded tail portion of said rod, and a clock-type spring co-axial with said rod having one end attached to a non-rotatable part of the brake assembly and the other end connected to said rod and nut assembly to rotate said nut relatively to said screw threaded tail portion to bring said friction pad into contact with said disc when said piston is in said fixed postion of rest.
2. The fluid operated spot-type disc brake assembly of claim 1 having a spring cover member closing one end of said cylinder and bearing against the piston to move said piston to said. position of rest.
3. The fluid operated spot-type disc brake as-- sembly of claim 1 in which the adjusting nutbears against the backing member and the clock-' type spring is secured at one end to the backing. member and at its other end to the nut.
4. The fluid operated spot-type disc brake as-- sembly of claim 1 in which said nut bears against.
said piston.
5. The fluid operated spot-type disc brake assembly of claim 1 in which said nut forms a part' of the backing member and the clock-type spring. is secured at one end to said rod and in which said rod is rotatable.
6. A fluid operated spot-type disc brake assembly which comprises a cylinder, a piston movable in said cylinder, said cylinder having means to stop said piston in a fixed position of rest and to admit fluid to move said piston from said position of rest to apply the brakes, a pair of radially spaced annular brake discs, each pair having a pad on each side of an associated disc, an axially aligned operating rod actuated by said piston and cylinder mechanism having a screw threaded tail portion, a non-rotatable backing member associated with said rod and movable thereby to bring the friction pads and discs into frictional engagement, an adjusting nut rotatable on the threaded tail portion of said rod, and a clock-type spring co-axial with said rod having one end attached to a non-rotatable part of the brake assembly and the other end connected to said rod and nut assembly to rotate said nut relatively to said screw threaded tail portion to bring said friction pad into contact with said discs when said piston is in said fixed position of rest.
HENRY JAMES BUTLER.
References Cited in the file of this patent UNITED STATES PATENTS Number Name Date Re. 19,876 Criley Mar. 3, 1936 1,495,714 Rath May 27, 1924 1,585,309 Monckmeier May 18, 1926 2,160,752 Oliver May 30, 1939 2,196,799 Keplinger Apr. 9, 1940 2,279,251 Scott-Iversen Apr. 7, 1942 2,366,093 Forbes Dec. 26, 1944 2,371,554 Scott-Iversen Mar. 13, 1945 2,376,685 Goepfrich May 22, 1945 2,419,113 Bricker Apr. 15, 1947 2,497,438 Butler Feb. 14, 1950 FOREIGN PATENTS Number Country Date 324,793 Italy Feb. 16, 1935
US767242A 1946-09-07 1947-08-07 Self-tightening disk brake Expired - Lifetime US2672223A (en)

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Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2762461A (en) * 1951-04-13 1956-09-11 Wagner Electric Corp Automatic adjusting mechanism for disc brakes
US2768710A (en) * 1952-06-21 1956-10-30 Dunlop Rubber Co Disc type brake for vehicles
US2820530A (en) * 1954-02-23 1958-01-21 Automotive Prod Co Ltd Operating mechanism for disc brakes
US2835350A (en) * 1952-09-04 1958-05-20 Dunlop Rubber Co Spot brakes
DE1146712B (en) * 1954-08-10 1963-04-04 Teves Kg Alfred Hydraulically operated partially-lined disc brake
US3459283A (en) * 1966-06-07 1969-08-05 Girling Ltd Diaphragm operated disc brake
US3966025A (en) * 1970-08-21 1976-06-29 Girling Limited Hydraulically operated disc brakes for vehicles
US4040506A (en) * 1970-08-21 1977-08-09 Girling Limited Hydraulically operated disc brakes for vehicles
US4175646A (en) * 1978-05-03 1979-11-27 Eikelberger Bruce H Electric parking brake

Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1495714A (en) * 1921-06-27 1924-05-27 August W Hornig Self-adjusting bearing lock
US1585309A (en) * 1924-05-14 1926-05-18 Gustav C Monckmeier Wear compensating bolt
USRE19876E (en) * 1936-03-03 Clutch
US2160752A (en) * 1937-02-12 1939-05-30 Oliver Albert Vere Friction clutch
US2196799A (en) * 1938-06-07 1940-04-09 Keplinger John Automatic brake adjuster
US2279251A (en) * 1939-08-28 1942-04-07 Rover Co Ltd Friction brake
US2366093A (en) * 1941-07-21 1944-12-26 Kelsey Hayes Wheel Co Brake
US2371554A (en) * 1938-10-01 1945-03-13 Rover Co Ltd Brake
US2376685A (en) * 1941-08-16 1945-05-22 Bendix Aviat Corp Brake actuating means
US2419113A (en) * 1944-04-26 1947-04-15 Wingfoot Corp Booster brake
US2497438A (en) * 1946-10-01 1950-02-14 Dunlop Rubber Co Fluid operated disk brake

Patent Citations (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
USRE19876E (en) * 1936-03-03 Clutch
US1495714A (en) * 1921-06-27 1924-05-27 August W Hornig Self-adjusting bearing lock
US1585309A (en) * 1924-05-14 1926-05-18 Gustav C Monckmeier Wear compensating bolt
US2160752A (en) * 1937-02-12 1939-05-30 Oliver Albert Vere Friction clutch
US2196799A (en) * 1938-06-07 1940-04-09 Keplinger John Automatic brake adjuster
US2371554A (en) * 1938-10-01 1945-03-13 Rover Co Ltd Brake
US2279251A (en) * 1939-08-28 1942-04-07 Rover Co Ltd Friction brake
US2366093A (en) * 1941-07-21 1944-12-26 Kelsey Hayes Wheel Co Brake
US2376685A (en) * 1941-08-16 1945-05-22 Bendix Aviat Corp Brake actuating means
US2419113A (en) * 1944-04-26 1947-04-15 Wingfoot Corp Booster brake
US2497438A (en) * 1946-10-01 1950-02-14 Dunlop Rubber Co Fluid operated disk brake

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2762461A (en) * 1951-04-13 1956-09-11 Wagner Electric Corp Automatic adjusting mechanism for disc brakes
US2768710A (en) * 1952-06-21 1956-10-30 Dunlop Rubber Co Disc type brake for vehicles
US2835350A (en) * 1952-09-04 1958-05-20 Dunlop Rubber Co Spot brakes
US2820530A (en) * 1954-02-23 1958-01-21 Automotive Prod Co Ltd Operating mechanism for disc brakes
DE1146712B (en) * 1954-08-10 1963-04-04 Teves Kg Alfred Hydraulically operated partially-lined disc brake
US3459283A (en) * 1966-06-07 1969-08-05 Girling Ltd Diaphragm operated disc brake
US3966025A (en) * 1970-08-21 1976-06-29 Girling Limited Hydraulically operated disc brakes for vehicles
US4040506A (en) * 1970-08-21 1977-08-09 Girling Limited Hydraulically operated disc brakes for vehicles
US4175646A (en) * 1978-05-03 1979-11-27 Eikelberger Bruce H Electric parking brake

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